TWI746079B - Anti-lock braking system and control method - Google Patents
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Abstract
一種防鎖死煞車系統及控制方法,於一控制模組在介入一車輛的煞車系統後執行,接收該車輛的一輪速信號與一加速度信號;根據該車輛的該輪速信號與該加速度信號計算一滑差回饋值,並根據一滑差目標值與該滑差回饋值之間的一滑差偏差值產生一基礎控制電壓;將該滑差回饋值進行微分補償以產生一滑差補償值,並以一查表方式將該滑差補償值對應一前饋電壓;將該基礎控制電壓加上該前饋電壓以產生一煞車控制電壓;以及將該煞車控制電壓輸出至一比例閥制動器,由該比例閥制動器根據該煞車控制電壓的大小調整一煞車壓力,以降低煞車時當ABS系統介入之車輪輪速變化。An anti-lock braking system and control method are executed after a control module intervenes in the braking system of a vehicle, and receives a wheel speed signal and an acceleration signal of the vehicle; calculates based on the wheel speed signal and the acceleration signal of the vehicle A slip feedback value, and a basic control voltage is generated according to a slip deviation value between a slip target value and the slip feedback value; the slip feedback value is differentially compensated to generate a slip compensation value, The slip compensation value corresponds to a feed-forward voltage in a table look-up method; the basic control voltage is added to the feed-forward voltage to generate a brake control voltage; and the brake control voltage is output to a proportional valve brake. The proportional valve brake adjusts a brake pressure according to the brake control voltage to reduce the wheel speed change when the ABS system intervenes during braking.
Description
本發明是有關一種煞車系統與方法,特別是指防鎖死煞車系統及控制方法。 The invention relates to a braking system and method, in particular to an anti-lock braking system and a control method.
請參考圖10,習知防鎖死煞車系統(Anti-lock Braking System,ABS)包含一電磁閥制動模組與一控制模組30,舉例來說,一車輛40可包含複數車輪,該複數車輪例如可包含一左前輪41、一右前輪42、一左後輪43及一右後輪44,對應的,該電磁閥制動模組可包含四個電磁閥制動器31,該控制模組30電連接該複數電磁閥制動器31,以控制該複數電磁閥制動器31施加煞車壓力於該複數車輪,此外,該控制模組30電連接該車輛的複數感知器(例如輪速計、加速度計...等)以獲取該車輛的行駛資訊(例如輪速、車速、加速度...等)。
Please refer to FIG. 10, the conventional Anti-lock Braking System (ABS) includes a solenoid valve brake module and a
以下簡述防鎖死煞車系統(ABS)的習知控制流程,該控制模組30先判斷是否有一煞車事件,即判斷該車輛的煞車踏板是否被踩下;當判斷有該煞車事件,該控制模組進一步判斷一車輛動態是否達到一預警門檻,舉例來說,該車輛動態可例如為所量測到車輪的輪減速度,該預警門檻即為輪減速度的一門檻值。另外,一般而言,滑差(slip differential)是指該車輛的車速與輪速的速度差異,可表示如下:
當該滑差過大,恐導致該車輛40在路面打滑,是以,當該控制模組30判斷該車輛動態達到該預警門檻,該控制模組30主動介入該車輛40的一
煞車系統,以對該電磁閥制動模組實施自動控制,此時該車輛40的煞車行為由該控制模組30掌握,藉此自動調整各該車輪的減慢速度及抑制滑差狀態,並避免各該車輪被鎖死,以期達到穩定該車輛的效果。
When the slip is too large, it may cause the
當該控制模組30介入該車輛的該煞車系統後,是驅動各該電磁閥制動器31於一釋放狀態與一煞車狀態作交替切換,其中,各該電磁閥制動器31操作於該釋放狀態時,為使煞車油通過一油壓閥而洩壓,例如洩壓後可使煞車壓力為零;相對的,各該電磁閥制動器31操作於該煞車狀態時,為使煞車油通過該油壓閥而增加煞車壓力。然而,習知防鎖死煞車系統仍包含以下缺點:
After the
1、各該電磁閥制動器31僅於該釋放狀態與該煞車狀態作交替切換,在其交替切換的過程中,各該電磁閥制動器31之該油壓閥承受油壓的衝擊(即相當於水鎚現象),容易造成各該電磁閥制動器31的損壞。
1. Each
2、當該控制模組30介入該車輛40的該煞車系統後,各該電磁閥制動器31僅於該釋放狀態與該煞車狀態作交替切換,對於各該車輪來說,其輪速忽快忽慢,故各該車輪的輪速高低起伏恐導致駕駛人或乘客在車上有間歇性急促震動的體驗,造成不適的感受。
2. After the
有鑒於此,本發明的主要目的是提供一種防鎖死煞車系統及控制方法,以期改善先前技術所述的兩項缺點。 In view of this, the main purpose of the present invention is to provide an anti-lock braking system and control method, in order to improve the two shortcomings described in the prior art.
本發明防鎖死煞車系統供應用於具有複數車輪的一車輛,該防鎖死煞車系統包含:一加速度計,輸出一加速度信號,該加速度信號反映該車輛的加速度;複數輪速計,分別對應該車輛的該複數車輪,各該輪速計分別輸出一輪速信號,該輪速信號反映各該車輪的輪速; 複數比例閥制動器,分別對應該車輛的該複數車輪,各該比例閥制動器分別接收一煞車控制電壓,並根據該煞車控制電壓的大小分別調整各該車輪的一煞車壓力;以及一控制模組,電連接該加速度計、該複數輪速計與該複數比例閥制動器,該控制模組在介入該車輛的一煞車系統後,根據各該輪速計的該輪速信號與該加速度計的該加速度信號產生各該比例閥制動器的該煞車控制電壓;其中,該控制模組根據各該輪速計的該輪速信號與該加速度信號計算一滑差回饋值,以及根據一滑差目標值與該滑差回饋值之間的一滑差偏差值產生一基礎控制電壓;該控制模組將該滑差回饋值進行微分補償以產生一滑差補償值,並以一查表方式將該滑差補償值對應至一前饋電壓;該控制模組將該基礎控制電壓加上該前饋電壓以產生該煞車控制電壓。 The anti-lock braking system of the present invention is provided for a vehicle with a plurality of wheels. The anti-lock braking system includes: an accelerometer, which outputs an acceleration signal, and the acceleration signal reflects the acceleration of the vehicle; multiple wheel speedometers, respectively In response to the plurality of wheels of the vehicle, each of the wheel speedometers respectively outputs a wheel speed signal, and the wheel speed signal reflects the wheel speed of each wheel; The plural proportional valve brakes respectively correspond to the plural wheels of the vehicle, each of the proportional valve brakes receives a brake control voltage, and adjusts a brake pressure of each wheel according to the magnitude of the brake control voltage; and a control module, The accelerometer, the multiple wheel speedometer and the multiple proportional valve brake are electrically connected. After the control module intervenes in a braking system of the vehicle, it is based on the wheel speed signal of each wheel speedometer and the acceleration of the accelerometer The signal generates the braking control voltage of each of the proportional valve brakes; wherein, the control module calculates a slip feedback value according to the wheel speed signal and the acceleration signal of each wheel speedometer, and according to a slip target value and the A slip deviation value between the slip feedback values generates a basic control voltage; the control module performs differential compensation on the slip feedback value to generate a slip compensation value, and compensates the slip by a look-up table The value corresponds to a feedforward voltage; the control module adds the basic control voltage to the feedforward voltage to generate the brake control voltage.
本發明防鎖死煞車控制方法於一控制模組在介入一車輛的一煞車系統後執行,該車輛包含複數車輪,該防鎖死煞車控制方法包含:接收該車輛的各該車輪的一輪速信號與一加速度信號;根據該車輛的該輪速信號與該加速度信號計算一滑差回饋值,並根據一滑差目標值與該滑差回饋值之間的一滑差偏差值產生一基礎控制電壓;將該滑差回饋值進行微分補償以產生一滑差補償值,並以一查表方式將該滑差補償值對應一前饋電壓;將該基礎控制電壓加上該前饋電壓以產生一煞車控制電壓;以及將該煞車控制電壓輸出至一比例閥制動器,由該比例閥制動器根據該煞車控制電壓的大小調整各該車輪的一煞車壓力。 The anti-lock braking control method of the present invention is executed after a control module intervenes in a braking system of a vehicle, the vehicle includes a plurality of wheels, and the anti-lock braking control method includes: receiving a wheel speed signal of each wheel of the vehicle And an acceleration signal; calculate a slip feedback value according to the wheel speed signal and the acceleration signal of the vehicle, and generate a basic control voltage according to a slip deviation value between a slip target value and the slip feedback value ; The slip feedback value is differentially compensated to generate a slip compensation value, and the slip compensation value corresponds to a feedforward voltage in a table look-up mode; the basic control voltage is added to the feedforward voltage to generate a Brake control voltage; and output the brake control voltage to a proportional valve brake, and the proportional valve brake adjusts a brake pressure of each wheel according to the magnitude of the brake control voltage.
和先前技術相比,本發明具有以下功效: Compared with the prior art, the present invention has the following effects:
1、有別於習知的各該電磁閥制動器,本發明的比例閥制動器非如習知的電磁閥制動器只能在釋放狀態與煞車狀態作交替切換而已,本發明的 比例閥制動器的煞車壓力隨著電壓大小而改變,故可更精細的調節煞車壓力,有效緩和各該比例閥制動器之油壓閥所承受的油壓衝擊,和習知的電磁閥制動器相比,本發明的比例閥制動器更不易因油壓衝擊而受損。 1. Different from the conventional solenoid valve brakes, the proportional valve brake of the present invention is not like the conventional solenoid valve brakes, which can only alternately switch between the released state and the brake state. The brake pressure of the proportional valve brake changes with the voltage, so the brake pressure can be adjusted more finely, and the oil pressure shock of the oil pressure valve of the proportional valve brake can be effectively alleviated. Compared with the conventional solenoid valve brake, The proportional valve brake of the present invention is less likely to be damaged due to hydraulic shock.
2、本發明透過該煞車控制電壓微調各該比例閥制動器的煞車壓力,該煞車控制電壓包含該前饋電壓的成分,該前饋電壓可有效降低各該車輪之輪速的變化量,進而能避免駕駛人或乘客在車上有間歇性急促震動的體驗,不致造成不適的感受。 2. The present invention fine-tunes the brake pressure of each proportional valve brake through the brake control voltage. The brake control voltage includes the component of the feedforward voltage. The feedforward voltage can effectively reduce the change of the wheel speed of each wheel, thereby enabling Avoid the experience of intermittent rapid vibration of the driver or passenger in the car, so as not to cause discomfort.
10:加速度計 10: Accelerometer
100:加速度信號 100: acceleration signal
11:輪速計 11: Wheel speedometer
110:輪速信號 110: Wheel speed signal
12:煞車制動模組 12: Brake brake module
120:比例閥制動器 120: Proportional valve brake
13:控制模組 13: Control module
20:車輛 20: Vehicle
21:左前輪 21: Left front wheel
22:右前輪 22: Right front wheel
23:左後輪 23: left rear wheel
24:右後輪 24: right rear wheel
30:控制模組 30: Control module
31:電磁閥制動器 31: Solenoid valve brake
40:車輛 40: Vehicle
41:左前輪 41: left front wheel
42:右前輪 42: right front wheel
43:左後輪 43: left rear wheel
44:右後輪 44: right rear wheel
V P :煞車控制電壓 V P : Brake control voltage
Slip FB :滑差回饋值 Slip FB : Slip feedback value
Slip TG :滑差目標值 Slip TG : Slip target value
Slip ERR :滑差偏差值 Slip ERR : slip deviation value
V B :基礎控制電壓 V B : Basic control voltage
Slip COMP :滑差補償值 Slip COMP : slip compensation value
Slip COMP_F :第一滑差補償值 Slip COMP_F : The first slip compensation value
Slip COMP_R :第二滑差補償值 Slip COMP_R : The second slip compensation value
V FF :前饋電壓 V FF : Feedforward voltage
V FF_F :第一前饋電壓 V FF_F : the first feedforward voltage
V FF_R :第二前饋電壓 V FF_R : second feedforward voltage
V est :車速 V est : Vehicle speed
W:輪速 W : Wheel speed
V LV_F :第一下限電壓 V LV_F : the first lower limit voltage
V UV_F :第一上限電壓 V UV_F : The first upper limit voltage
S L_F :第一滑差下限值 S L_F : the lower limit of the first slip
S U_F :第一滑差上限值 S U_F : the upper limit of the first slip
V LV_R :第二下限電壓 V LV_R : The second lower limit voltage
V UV_R :第二上限電壓 V UV_R : The second upper limit voltage
S L_R :第二滑差下限值 S L_R : The second lower limit of slip
S U_R :第二滑差上限值 S U_R : The second upper limit of slip
Σ:總和運算 Σ: Sum operation
圖1:本發明防鎖死煞車系統的實施例的方塊示意圖。 Figure 1: A block diagram of an embodiment of the anti-lock braking system of the present invention.
圖2:本發明防鎖死煞車系統應用於一車輛的示意圖。 Figure 2: A schematic diagram of the anti-lock braking system of the present invention applied to a vehicle.
圖3:本發明防鎖死煞車控制方法的實施例的流程示意圖。 Fig. 3: A schematic flowchart of an embodiment of an anti-lock braking control method of the present invention.
圖4:本發明產生該煞車控制電壓給該比例閥制動器的流程示意圖。 Fig. 4: The present invention generates the brake control voltage to the proportional valve brake.
圖5:圖4中的PID控制單元在S域(S-domain)的運算示意圖。 Fig. 5: A schematic diagram of the operation of the PID control unit in Fig. 4 in the S-domain.
圖6:本發明實施例中的第一對照表的示意圖。 Fig. 6: A schematic diagram of a first comparison table in an embodiment of the present invention.
圖7:本發明實施例中的第二對照表的示意圖。 Fig. 7: A schematic diagram of a second comparison table in an embodiment of the present invention.
圖8A:車速、左前輪與右前輪的波形示意圖(煞車控制電壓未包含前饋電壓)。 Figure 8A: Waveform diagram of vehicle speed, left front wheel and right front wheel (the brake control voltage does not include the feedforward voltage).
圖8B:車速、左後輪與右後輪的波形示意圖(煞車控制電壓未包含前饋電壓)。 Figure 8B: Waveform diagram of vehicle speed, left rear wheel and right rear wheel (the brake control voltage does not include the feedforward voltage).
圖9A:車速、左前輪與右前輪的波形示意圖(煞車控制電壓包含前饋電壓)。 Figure 9A: Waveform diagram of vehicle speed, left front wheel and right front wheel (brake control voltage includes feedforward voltage).
圖9B:車速、左後輪與右後輪的波形示意圖(煞車控制電壓包含前饋電壓)。 Fig. 9B: Waveform diagram of vehicle speed, left rear wheel and right rear wheel (brake control voltage includes feedforward voltage).
圖10:習知防鎖死煞車系統應用於一車輛的示意圖。 Figure 10: A schematic diagram of a conventional anti-lock braking system applied to a vehicle.
請參考圖1與圖2,本發明防鎖死煞車系統(Anti-lock Braking System,ABS)的實施例包含一加速度計10、複數輪速計11、一煞車制動模組12與一控制模組13。舉例來說,本發明防鎖死煞車系統供應用於一車輛20,該車輛20具有複數車輪,該煞車制動模組12包含分別對應於該複數車輪的複數比例閥制動器120,各該比例閥制動器120用以調整各該車輪煞車壓力。
Please refer to Figures 1 and 2, an embodiment of the Anti-lock Braking System (ABS) of the present invention includes an
請參考圖2,該車輛20的該複數車輪可包含(但不限於)複數前車輪與複數後車輪,該複數前車輪可包含一左前輪21及一右前輪22,該複數後車輪可包含一左後輪23及一右後輪24。對應的,該煞車制動模組12可包含四個比例閥制動器120,以分別調整該左前輪21、該右前輪22、該左後輪23及該右後輪24煞車壓力。
Please refer to FIG. 2, the plurality of wheels of the
需說明的是,請參考圖1,本發明的該加速度計10、該複數輪速計11、該煞車制動模組12與各該比例閥制動器120的工作原理為所屬技術領域中的通常知識,在此不加以詳述,僅簡述如後。該加速度計10輸出一加速度信號100,該加速度信號100反映該車輛20的加速度;該複數輪速計11分別對應該車輛20的該複數車輪,各該輪速計11分別輸出一輪速信號110,該輪速信號110反映各該車輪的輪速;各該比例閥制動器120接收一煞車控制電壓V P ,並根據該煞車控制電壓V P 的大小調整各該車輪的一煞車壓力。當該煞車控制電壓V P 越大,各該比例閥制動器120提供的煞車壓力越小,換言之,若要提高各該比例閥制動器120的洩壓程度,可提升該煞車控制電壓V P 的電壓值;相對的,若要控制各該比例閥制動器120增壓,可降低各該煞車控制電壓V P 的電壓值。
It should be noted that, referring to FIG. 1, the working principles of the
請配合參考圖1與圖2,該控制模組13電連接該加速度計10、該複數輪速計11與該複數比例閥制動器120,該控制模組13根據各該輪速計11的
該輪速信號110與該加速度計10的該加速度信號100產生各該比例閥制動器120的該煞車控制電壓V P ,藉此個別控制各該車輪的煞車壓力,以下說明僅以控制其中之一車輪的情境為例,其他車輪的控制情形可依此類推。是以,整體而言,該車輛20的該左前輪21、該右前輪22、該左後輪23及該右後輪24都被獨立控制,故能有效縮短煞車距離,並提高煞車效率。
1 and 2, the
請配合參考圖1至圖3,本發明防鎖死煞車控制方法的實施例係於該控制模組13執行,其中,需說明的是,本發明防鎖死煞車控制方法是在該控制模組13主動介入該車輛20的一煞車系統之後才實施。如同習知的防鎖死煞車系統(ABS),本發明的該控制模組13主動介入該煞車系統的條件為所屬技術領域中的通常知識,在此容不詳述。
Please refer to FIGS. 1 to 3 in conjunction. The embodiment of the anti-lock braking control method of the present invention is implemented in the
請參考圖3與圖4,本發明防鎖死煞車控制方法包含以下步驟: Please refer to FIG. 3 and FIG. 4, the anti-lock braking control method of the present invention includes the following steps:
步驟S01:該控制模組13接收各該輪速計11的各該輪速信號110與該加速度信號100。如前所述,該輪速信號110是從該輪速計11接收的,其反映各該車輪當下的輪速;該加速度信號100是從該加速度計10接收的,其反映該車輛20當下的加速度。
Step S01: The
步驟S02:該控制模組13根據各該輪速計11的該輪速信號110與該加速度信號100計算一滑差回饋值Slip FB ,以及根據一滑差目標值Slip TG 與該滑差回饋Slip FB 值之間的一滑差偏差值Slip ERR 產生一基礎控制電壓V B 。本發明的實施例中,該滑差回饋值(SlipFB)可表示如下:
上式中,V est 為該車輛20的車速,W為各該車輪的輪速。其中,各該車輪的輪速W可表示如下:
上式中,vrpm即為該輪速信號110,vrpm反映各該車輪在單位時間(每分鐘)內的轉動圈數,r為各該車輪的半徑(單位:公尺)。
In the above formula, v rpm is the
本發明的實施例中,該車輛的車速V est 為包含時間(t)的函數,較佳的可表示如下:
上式為引用美國汽車工程師協會(Society of Automotive Engineers,SAE)的公開文獻:
其中,;k表示數據的時間點,例如(k)表示當下時間點的車速,(k-1)表示上一時間點的車速;K 2代表權重,0 K 2 1;r est 為各該車輪的半徑;ω(k)為各該車輪的輪速,即W=ω(k);a meas 為該車輛20的加速度(即:該加速度信號100)。簡言之,該車輛的車速V est 為根據該輪速信號110與該加速度信號100所產生的一估計值,藉由權重K 2的設定,可決定車速V est 的估算較仰賴各該車輪的輪速W或該車輛20的加速度a meas 。
in, ; K represents the time point of the data, for example ( k ) represents the vehicle speed at the current point in time, ( k -1) represents the vehicle speed at the previous point in time; K 2 represents the weight, 0
該滑差目標值Slip TG 為一預設值,其代表的意義為透過本發明實施煞車控制時所要追求的滑差值,例如該滑差目標值Slip TG 可為小於或等於20%,惟不以20%為限。是以,滑差偏差值Slip ERR 產可表示如下: Slip ERR =Slip TG -Slip FB The slip target value Slip TG is a preset value, and its representative meaning is the slip value to be pursued when the brake control is implemented through the present invention. For example, the slip target value Slip TG can be less than or equal to 20%, but not The limit is 20%. Therefore, the slip deviation value Slip ERR can be expressed as follows: Slip ERR = Slip TG - Slip FB
該控制模組13根據該滑差偏差值Slip ERR 通過一比例-積分-微分(PID)控制單元產生一基礎控制電壓V B ,該PID控制單元的運算為所屬技術領域中的通常知識,例如利用圖5以古典控制架構進行最小化誤差值的計算並送出修正量,容不詳述。其中,比例增益的數值範圍較佳的可在0至5之間(包含0與5),積分增益的數值範圍較佳的可在0至1之間(包含0與1),微分增益的數值範圍較佳的可在0至1之間(包含0與1)。
The
步驟S03:該控制模組13將該滑差回饋值Slip FB 進行微分補償以產生一滑差補償值Slip COMP ,並以一查表方式將該滑差補償值Slip COMP 對應至一前饋電壓V FF 。在本發明的實施例中,該滑差補償值Slip COMP 可表示如下:
上式中,C為權重,0C1,不同的各該車輪所對應的C值不同,舉例來說,該複數前車輪(包含該左前輪21與該右前輪22)的C值大於該複數後車輪(包含該左後輪23與該右後輪24)的C值,較佳的,該複數前車輪的C值可為0.6,該複數後車輪的C值可為0.1,但不以前述數值為限。
In the above formula, C is the weight, 0
關於該查表方式,即該控制模組13儲存一對照表,該對照表使一筆滑差補償值Slip COMP 可對應至一筆前饋電壓V FF 的電壓大小。一般而言,該前饋電壓V FF 的電壓值為界於0伏特(V)與10V,即0V V FF 10V,而各該比例閥制動器120的操作電壓範圍例如可在3.5V至9V之間(包含3.5V及9V)。當該滑差補償值Slip COMP 越大,該前饋電壓V FF 的電壓大小也越大,故該滑差補償值Slip COMP 與該前饋電壓V FF 可具有正比比例關係。
Regarding the table look-up method, that is, the
本發明的實施例中,該控制模組13儲存複數對照表,包含一第一對照表與一第二對照表,該第一對照表對應該複數前車輪,該第二對照表對應該複數後車輪。
In the embodiment of the present invention, the
請配合參考圖6,顯示該第一對照表所包含的數據,詳述如後:從如圖1所示的該加速度信號100與該左前輪21或該右前輪22的該輪速信號110運算而得的該滑差補償值Slip COMP 定義為一第一滑差補償值Slip COMP_F ,且對應於該左前輪21與該右前輪22的該前饋電壓V FF 定義為一第一前饋電壓V FF_F 。當該第一滑差補償值Slip COMP_F 等於一第一滑差下限值S L_F (例如10%),該第一前饋電壓V FF_F 對應為等於一第一下限電壓V LV_F (例如5V);當該第一滑差補償值Slip COMP_F 等於一第一滑差上限值S U_F (例如60%),該第一前饋電壓V FF_F 對應為等於一第一上限電壓V UV_F (例如10V);當Slip COMP_F <S L_F 時,該第一前饋電壓V FF_F 對應為等於0V;當S L_F <Slip COMP_F <S U_F ,該第一滑差補償值Slip COMP_F 與該第一前饋電壓V FF_F 具有一正比比例的線性關係,且V LV_F <V FF_F <V UV_F ;當Slip COMP_F >S U_F 時,該第一前饋電壓V FF_F 對應為等於該第一上限電壓V UV_F 。其中,為避免洩壓不足,該上限電壓V UV_F 可設定為大於各該比例閥制動器120的操作電壓範圍的一最大值,如前所述,因為各該比例閥制動器120的操作電壓範圍可在3.5V至9V之間,該上限電壓V UV_F 可設定為10V。
Please refer to FIG. 6 to display the data contained in the first comparison table. The details are as follows: calculate from the
在本發明的實施例中,經過該控制模組13的參數設定,使該第一對照表包含該第一下限電壓V LV_F 、該第一上限電壓V UV_F 、該第一滑差下限值S L_F 與該第一滑差上限值S U_F ;當該第一滑差補償值Slip COMP_F 界於該第一滑差下限值S L_F 與該第一滑差上限值S U_F 之間,該第一滑差補償值Slip COMP_F 與該第一前饋電壓V FF_F 的該正比比例的線性關係即可確定。
In the embodiment of the present invention, after the parameter setting of the
請配合參考圖7,顯示該第二對照表所包含的數據,詳述如後:從如圖1所示的該加速度信號100與該左後輪23或該右後輪24的該輪速信號110運算而得的該滑差補償值Slip COMP 定義為一第二滑差補償值Slip COMP_R ,且對應於該左後輪23與該右後輪24的該前饋電壓V FF 定義為一第二前饋電壓V FF_R 。當該第二滑差補償值Slip COMP_R 等於一第二滑差下限值S L_R (例如10%),該第二前饋電壓V FF_R 對應為等於一第二下限電壓V LV_R (例如5V);當該第二滑差補償值Slip COMP_R 等於一第二滑差上限值S U_R (例如30%),該第二前饋電壓V FF_R 對應為等於一第二上限電壓V UV_R (例如10V);當Slip COMP_R <S L_R 時,該第二前饋電壓V FF_R 對應為等於0V;當S L_R <Slip COMP_R <S U_R ,該第二滑差補償值Slip COMP_R 與該第二前饋電壓V FF_R 具有一正比比例的線性關係,且V LV_R <V FF_R <V UV_R ;當Slip COMP_R >S U_R 時,該第二前饋電壓V FF_R 對應為等於該第一上限電壓V UV_R 。同樣的,為避免洩壓不足,該上限電壓V UV_R 可設定為10V。
Please refer to FIG. 7 to display the data contained in the second comparison table. The details are as follows: from the
在本發明的實施例中,經過該控制模組13的參數設定,使該第二對照表包含該第二下限電壓V LV_R 、該第二上限電壓V UV_R 、該第二滑差下限值S L_R 與該第二滑差上限值S U_R ;當該第二滑差補償值Slip COMP_R 界於該第二滑差下限值S L_R 與該第二滑差上限值S U_R 之間,該第二滑差補償值Slip COMP_R 與該第二前饋電壓V FF_R 的該正比比例的線性關係即可確定。
In the embodiment of the present invention, after the parameter setting of the
步驟S04:該控制模組13將該基礎控制電壓V B 加上該前饋電壓V FF 以產生該煞車控制電壓V P ,即可表示如下:V P =V B +V FF Step S04: The
本發明的實施例中,對應控制各該前車輪的該煞車控制電壓V P 定義為一第一煞車控制電壓V P_F ,可表示如下: V P_F =V B +V FF_F In the embodiment of the present invention, the brake control voltage V P corresponding to each of the front wheels is defined as a first brake control voltage V P_F , which can be expressed as follows: V P_F = V B + V FF_F
對應控制各該後車輪的該煞車控制電壓V P 定義為一第二煞車控制電壓V P_R ,可表示如下:V P_R =V B +V FF_R The brake control voltage V P corresponding to each of the rear wheels is defined as a second brake control voltage V P_R , which can be expressed as follows: V P_R = V B + V FF_R
綜上所述,該控制模組13輸出該第一煞車控制電壓V P_F 驅動各該前車輪(即:該左前輪21或該右前輪22)的該比例閥制動器120,以及輸出該第二煞車控制電壓V P_R 驅動各該後車輪(即:該左後輪23或該右後輪24)的該比例閥制動器120。各該煞車控制電壓V P_F 、V P_R 包含各該前饋電壓V FF_F 、V FF_R 的成分,而各該前饋電壓V FF_F 、V FF_R 是從各該滑差補償值Slip COMP_F 、Slip COMP_R 運算而來。以下參考圖8A、圖8B、圖9A與圖9B的實測資料,雖然各該車輪的輪速波形彼此交錯或重疊,只透過觀察各該車輪的輪速波形趨勢,仍可看出各該前饋電壓V FF_F 、V FF_R 的功效。
In summary, the
請參考圖2、圖8A與圖8B,其中圖8A與圖8B的波形是在一第一煞車事件的實測資料,故圖8A與圖8B的車速波形是一致的,僅將該左前輪21與該右前輪22的輪速波形揭露於圖8A,另將該左後輪23與該右後輪24的輪速波形揭露於圖8B,在該第一煞車事件中,各該煞車控制電壓V P_F 、V P_R 未包含各該前饋電壓V FF_F 、V FF_R 。如圖8A與圖8B,在約第6秒時,該控制模組13介入該車輛20的該煞車系統,故該車輛20的車速從約時速93公里隨著時間遞減,請參考圖8A,該左前輪21與該右前輪22的輪速在第6.5秒至第7秒之間的振幅較大,大約第7.2秒之後的振幅較小;請參考圖8B,該左後輪23與該右後輪24的輪速的振幅都比該左前輪21與該右前輪22的振幅更大。
Please refer to Figures 2, 8A and 8B, where the waveforms in Figures 8A and 8B are measured data of a first braking event, so the vehicle speed waveforms in Figures 8A and 8B are consistent, only the
請參考圖2、圖9A與圖9B,其中圖9A與圖9B的波形是在一第二煞車事件的實測資料,故圖9A與圖9B的車速波形是一致的,僅將該左前輪21與
該右前輪22的輪速波形揭露於圖9A,另將該左後輪23與該右後輪24的輪速波形揭露於圖9B,在該第二煞車事件中,各該煞車控制電壓V P_F 、V P_R 包含各該前饋電壓V FF_F 、V FF_R ;由此可見,該第二煞車事件與該第一煞車事件分別為兩次不同的煞車事件,採用的煞車控制電壓彼此不同。如圖9A與圖9B,在約第2.4秒時,該控制模組13介入該車輛20的該煞車系統,故該車輛20的車速從約時速97公里隨著時間遞減,請參考圖9A與圖9B,該左前輪21、該右前輪22、該左後輪23與該右後輪35的輪速隨著時間穩定遞減,尤其如圖9A所示,該左前輪21與該右前輪22的輪速幾乎一致。
Please refer to Figure 2, Figure 9A and Figure 9B, where the waveforms of Figures 9A and 9B are measured data of a second braking event, so the vehicle speed waveforms of Figures 9A and 9B are consistent, only the
將圖8A與圖9A的輪速相比,圖9A沒有如圖8A在第6.5秒至第7秒之間的較大振幅現象,故各該前饋電壓V FF_F 確實改善該左前輪21與該右前輪22的輪速振盪現象。另將圖8B與圖9B相比,圖9B的該左後輪23與該右後輪24的輪速振幅獲得顯著的降低。綜合來看,對於各該車輪來說,本發明的該控制模組13將該基礎控制電壓V B 加上該前饋電壓V FF 以產生該煞車控制電壓V P ,使各該煞車控制電壓V P 包含各該前饋電壓V FF ,由該前饋電壓V FF 輔助改善各該車輪的輪速振盪現象,進而能避免駕駛人或乘客在車上有間歇性急促震動的體驗,不致造成不適的感受。
Comparing the wheel speeds of Fig. 8A with Fig. 9A, Fig. 9A does not have the phenomenon of large amplitude between 6.5 seconds and 7 seconds as shown in Fig. 8A, so each of the feedforward voltages V FF_F does improve the
另請參考圖6與圖7,本發明的實例中,圖7所示的該第二滑差上限值S U_R 低於圖6所示的該第一滑差上限值S U_F ,表示該左後輪23與該右後輪24在較低的滑差狀態(例如10%至60%之間)時的各該前饋電壓V FF_R 較高,故該左後輪23與該右後輪24的洩壓壓力較大(即:煞車壓力較小)。本發明將該第二滑差上限值S U_R 設定為低於該第一滑差上限值S U_F 的理由在於,請參考圖2、圖9A與圖9B,相較於該左前輪21與該右前輪22,當該左後輪23與該右後輪24被鎖死,該車輛20的車尾恐發生左右偏擺的現象,故本發明透過S U_R <S U_F 的設定,使該左後輪23與該右後輪24的煞車壓力更低,避免該左後輪23與該右後輪
24因煞車壓力較大而更容易被鎖死,能有效穩定該車輛20的車身,改善該車輛20的車尾左右偏擺的現象。
Please also refer to FIG. 6 and FIG. 7. In an example of the present invention, the second upper limit slip value S U_R shown in FIG. 7 is lower than the first upper limit slip value S U_F shown in FIG. When the left
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TWM483197U (en) * | 2014-03-17 | 2014-08-01 | Bo-Xiong Hong | Electric-propelled anti-skid braking system and anti-skid brake control device |
CN110308656A (en) * | 2019-07-17 | 2019-10-08 | 江苏理工学院 | The fuzzy immune PID control method of anti-blocking brake system of automobile |
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2020
- 2020-07-22 TW TW109124807A patent/TWI746079B/en active
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EP0159284A1 (en) * | 1984-02-24 | 1985-10-23 | Licentia Patent-Verwaltungs-GmbH | Control method for the drive or brake power of the traction motor of an electric traction vehicle without running axles at the static friction limit of the wheels |
TWM249389U (en) * | 2004-01-13 | 2004-11-01 | Yih Dar Techologies Co Ltd | Improved reflective mirror structure of back-projection type TV |
CN101867339A (en) * | 2010-04-09 | 2010-10-20 | 奇瑞汽车股份有限公司 | Motor control method of electronic mechanical braking system |
TWM483197U (en) * | 2014-03-17 | 2014-08-01 | Bo-Xiong Hong | Electric-propelled anti-skid braking system and anti-skid brake control device |
CN110308656A (en) * | 2019-07-17 | 2019-10-08 | 江苏理工学院 | The fuzzy immune PID control method of anti-blocking brake system of automobile |
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